CN221198142U - Plate for plate type heat exchanger - Google Patents
Plate for plate type heat exchanger Download PDFInfo
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- CN221198142U CN221198142U CN202322959816.4U CN202322959816U CN221198142U CN 221198142 U CN221198142 U CN 221198142U CN 202322959816 U CN202322959816 U CN 202322959816U CN 221198142 U CN221198142 U CN 221198142U
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- herringbone
- flow guiding
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- 239000000758 substrate Substances 0.000 claims abstract description 17
- 238000007789 sealing Methods 0.000 claims abstract description 7
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 48
- 230000001154 acute effect Effects 0.000 claims description 12
- 229910000881 Cu alloy Inorganic materials 0.000 claims description 3
- -1 aluminium zinc copper Chemical compound 0.000 claims description 3
- 238000012546 transfer Methods 0.000 abstract description 16
- 239000002585 base Substances 0.000 description 12
- 238000000034 method Methods 0.000 description 5
- 238000013461 design Methods 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- QAOWNCQODCNURD-UHFFFAOYSA-N Sulfuric acid Chemical compound OS(O)(=O)=O QAOWNCQODCNURD-UHFFFAOYSA-N 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 239000006244 Medium Thermal Substances 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 239000003513 alkali Substances 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 238000005189 flocculation Methods 0.000 description 1
- 230000016615 flocculation Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000002209 hydrophobic effect Effects 0.000 description 1
- 238000012966 insertion method Methods 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000009856 non-ferrous metallurgy Methods 0.000 description 1
- 238000011056 performance test Methods 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000007670 refining Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
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- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The utility model discloses a plate for a plate heat exchanger, which comprises a substrate, wherein two ends of the symmetrical substrate are provided with corner hole areas, flow guiding areas and heat conducting areas; a herringbone seal groove is formed at the joint of the angular hole area and the flow guiding area, and the joint of the flow guiding area and the heat conducting area is an arc line; the flow guiding area is provided with a plurality of bulges along the plate surfaces at two sides of the substrate, and the bulges are vertical to the herringbone sealing groove, parallel to the herringbone sealing groove or inclined at any angle; the heat conduction area is formed by splicing a plurality of detachable removing blocks. The plate provided by the utility model can select the length of the base plate according to the requirement by splicing the removing blocks, and is suitable for plate heat exchangers with different sizes; the flow guiding area can guide the heat transfer medium to enter the heat conducting area for heat transfer, and plates of different forms of flow guiding areas are selected according to the needs, so that the heat transfer device is suitable for selection of different heat transfer working conditions.
Description
Technical Field
The utility model relates to the technical field of heat exchange equipment, in particular to a plate for a plate type heat exchanger.
Background
The plate heat exchanger is a high-efficiency heat exchanger formed by stacking a series of metal sheets with a certain corrugated shape, is equipment for heating and cooling media, such as a production process, a heat supply and refrigeration system and the like, and is widely applied to various industries related to national economy and life such as oil refining, chemical industry, steel, nonferrous metallurgy, alkali production, sugar production, sulfuric acid, thermal power plants, nuclear power plants, food, papermaking, military industry, ships, urban heat supply and refrigeration and the like, and the core component of the plate heat exchanger is a heat exchange plate, wherein a thin rectangular channel is formed between the plates, and heat exchange is carried out through the plates. The plate heat exchanger is ideal equipment for liquid-liquid and liquid-gas heat exchange. The heat exchanger has the characteristics of high heat exchange efficiency, small heat loss, compact and light structure, small occupied area, wide application, long service life and the like. Under the same pressure loss, the heat transfer coefficient is 3-5 times higher than that of the tubular heat exchanger, the occupied area is one third of that of the tubular heat exchanger, and the heat recovery rate can be up to more than 90%.
The heat exchanger plate provides a heat exchange medium flow channel and a heat exchange surface for the plate heat exchanger through a unique corrugated design, so that fluid is forced to form rotary three-dimensional flow in the plate grooves, and flocculation flow is generated under the condition of low Reynolds number, so that the heat exchange coefficient is effectively improved, but higher flow resistance and higher pump power are caused.
Therefore, how to provide a plate for a plate heat exchanger, which reduces flow resistance and pump power with an increased heat exchange coefficient, is a problem to be solved by the person skilled in the art.
Disclosure of utility model
In view of the above, the present utility model provides a plate for a plate heat exchanger, which aims to solve the above technical problems.
In order to achieve the above purpose, the present utility model adopts the following technical scheme:
A plate for a plate heat exchanger comprises a base plate, wherein
The two ends of the substrate are symmetrically provided with corner hole areas, flow guiding areas and heat conducting areas; a herringbone seal groove is formed at the joint of the angular hole area and the flow guiding area, and the joint of the flow guiding area and the heat conducting area is an arc line;
The flow guiding area is provided with a plurality of bulges along the plate surfaces on two sides of the substrate, and the bulges are vertical, parallel or inclined at any angle with the herringbone seal groove
The heat conduction area is formed by splicing a plurality of detachable removing blocks, a plurality of continuous herringbone waves are arranged on the plate surfaces of the removing blocks, and the included angles of the centers of the herringbone waves in the horizontal direction are acute angles, obtuse angles or combination of the acute angles and the obtuse angles so as to form three different flow channels.
The technical scheme has the advantages that the length of the base plate can be selected according to the requirement by splicing the removing blocks, so that the plate heat exchanger is suitable for plate heat exchangers with different sizes; the herringbone corrugation can form three different liquid flow channels, when the obtuse angle herringbone corrugation is selected, the herringbone corrugation has the characteristics of high heat transfer coefficient and high resistance, when the acute angle herringbone corrugation is selected, the herringbone corrugation has the characteristics of low heat transfer coefficient and low resistance, when the herringbone corrugation combining the acute angle with the obtuse angle is selected, the herringbone corrugation has the characteristics of medium heat transfer coefficient and medium resistance, the herringbone corrugation with different angles can be selected according to the needs of users, the application range is wider, the heat transfer coefficient can be improved through the arrangement of the herringbone corrugation, and meanwhile, the flow resistance and the pump power of liquid are reduced.
Preferably, in the plate for a plate heat exchanger, the angular hole area is provided with a hot water inlet, a cold water outlet, a hot water outlet, a cold water inlet and protection ripples, wherein the hot water inlet and the hot water outlet, the cold water outlet and the cold water inlet are symmetrically arranged along two sides of the X axis of the base plate, the hot water inlet, the hot water outlet and the cold water outlet, and the cold water inlet are symmetrically arranged along two sides of the Y axis of the base plate, and the protection ripples and the diversion area are separated by the herringbone seal grooves. When the plate heat exchanger is used, cold water medium enters from below and goes out from above, hot water medium enters from above and goes out from below, the flowing mode of the medium in the channel is pure countercurrent, and the heat exchange effect of the plate heat exchanger can be effectively ensured.
Preferably, in the plate for a plate heat exchanger, the chevron-shaped corrugation has a corrugation depth of 4 to 20mm.
Preferably, in the plate for the plate heat exchanger, the distance between two adjacent herringbone waves is 10-15 mm.
Preferably, in the above plate for a plate heat exchanger, the protrusions are one or more of round, square or drop-shaped.
Preferably, in the plate for a plate heat exchanger, a dovetail groove is formed at an end of a short side of the base plate. Five-point positioning can be realized by the dovetail groove, the disassembly of the plate sheet at any position on the guide rod of the heat exchanger can be realized, the labor intensity and time for assembling, maintaining and replacing spare parts of products are greatly reduced, and the working efficiency is improved.
Preferably, in the plate for a plate heat exchanger, the thickness of the substrate is 0.4 to 0.7mm.
Preferably, in the plate for the plate heat exchanger, the substrate is made of an aluminum zinc copper alloy plate through a die. The plate is integrally formed by one-step pressing, and all the plates are uniformly formed by one-step pressing in order to control the forming pressure and the forming size. The sheet is cold-stamped on a press, a small amount of residual stress is generated in the cold-stamping forming process, and in order to reduce the residual stress, the requirements of processing precision and surface finish are strictly controlled in the links of selecting press die materials, processing the dies and the like, and the sheet is stored for a certain time after the sheet is formed, so that the residual stress is eliminated.
Compared with the prior art, the plate for the plate heat exchanger has the following beneficial effects:
1. The thermal design of the plate can ensure that the equipment can obtain good hydraulic and thermal performances when the device is started, runs under low load and low flow rate. Through performance test, the heat transfer coefficient can reach more than 6000W/m 2K.
2. And (3) integrally forming: the integral design of the plate is seamless, and the assembly precision and the good sealing performance of the equipment are ensured;
4. Pure countercurrent: the cold side medium enters from the lower part and goes out from the upper part, the hot side medium enters from the upper part and goes out from the lower part, and the flow in the channel is pure countercurrent;
5. Unilateral/diagonal flow: the inlet/outlet of the same medium is diagonal on one/both sides.
Drawings
In order to more clearly illustrate the embodiments of the present utility model or the technical solutions in the prior art, the drawings that are required to be used in the embodiments or the description of the prior art will be briefly described below, and it is obvious that the drawings in the following description are only embodiments of the present utility model, and that other drawings can be obtained according to the provided drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic view of a plate structure according to the present utility model;
FIG. 2 is a schematic view of a herringbone corrugated structure of a plate sheet provided by the utility model;
FIG. 3 is a schematic view of an obtuse angle herringbone ripple structure provided by the utility model;
FIG. 4 is a schematic view of an acute angle chevron corrugated structure provided by the present utility model;
fig. 5 is a schematic view of a herringbone corrugated structure combining obtuse angles and acute angles.
FIG. 6 is a schematic view of a flow guiding area according to the present utility model;
FIG. 7 is a schematic view of the corner hole area structure provided by the present utility model;
FIG. 8 is a schematic view of the plate structure of example 2 according to the present utility model;
FIG. 9 is a schematic view of the structure of the flow guiding region in embodiment 2 according to the present utility model;
FIG. 10 is a schematic view of the structure of the corner hole region in embodiment 2 according to the present utility model;
FIG. 11 is a schematic view of the plate structure of example 3 according to the present utility model;
FIG. 12 is a schematic view of the structure of the flow guiding region in embodiment 3 according to the present utility model;
Fig. 13 is a schematic view of the structure of the corner hole area in embodiment 3 according to the present utility model.
Wherein:
1-a substrate; 2-a diversion area; 3-a heat transfer area; 31-removing blocks; 32-arc line; 33-chevron corrugations; 331-center angle; 332-corrugation depth; 4-a dovetail groove; 5-corner hole region; 51-a hot water inlet; 52-a cold water outlet; 53-hot water outlet; 54-cold water inlet; 55-protecting against ripples; 6-herringbone seal groove.
Detailed Description
The following description of the embodiments of the present utility model will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present utility model, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.
Example 1:
Referring to fig. 1, the embodiment of the present utility model discloses a plate for a plate heat exchanger, comprising a base plate 1, wherein
The two ends of the symmetrical substrate 1 are provided with an angular hole area 5, a flow guiding area 2 and a heat conducting area 3; the connection part of the angular hole area 5 and the flow guiding area 2 forms a herringbone seal groove 6, and the connection part of the flow guiding area 2 and the heat conducting area 3 is an arc line 32;
The diversion area 2 is provided with a plurality of bulges along the two side surfaces of the base plate 1, and the bulges are vertical to the herringbone seal groove 6, parallel to the herringbone seal groove or inclined at any angle;
the heat transfer area 3 is formed by splicing a plurality of detachable removing blocks 31, a plurality of continuous herringbone waves 33 are arranged on the plate surfaces of the plurality of removing blocks 31, and the central included angle 331 of the herringbone waves 33 in the horizontal direction is an acute angle, an obtuse angle or a combination of the acute angle and the obtuse angle so as to form three different flow channels.
Referring to fig. 2 and 3, the herringbone corrugation is obtuse, the angle is 127 degrees, and the herringbone corrugation has the characteristics of high heat transfer coefficient and high resistance drop; referring to fig. 4, the herringbone corrugation is in an acute angle and has an angle of 56 degrees, the herringbone corrugation has the characteristics of low heat transfer coefficient and low resistance drop, and referring to fig. 5, the herringbone corrugation is in a form of combining an acute angle and an obtuse angle, has the characteristics of medium heat transfer coefficient and medium resistance drop, and can select herringbone corrugations with different angles according to use conditions and user requirements.
In order to further optimize the above technical scheme, the medium in the heat exchanger is in a pure countercurrent state, the heat exchange effect of the heat exchanger is ensured, the corner hole area 5 is provided with a hot water inlet 51, a cold water outlet 52, a hot water outlet 53, a cold water inlet 54 and a protection ripple 55, wherein the hot water inlet 51, the hot water outlet 53, the cold water outlet 52 and the cold water inlet 54 are symmetrically arranged along the two sides of the X axis of the base plate 1, the hot water inlet 51, the hot water outlet 53, the cold water outlet 52 and the cold water inlet 54 are symmetrically arranged along the two sides of the Y axis of the base plate 1, and the protection ripple 55 and the diversion area 2 are separated by the herringbone seal groove 6.
In the figure 1, the X axis is the short side of the base plate, the Y axis is the long side of the base plate, the mounting direction of the plate is the direction of illustration, the cold water inlet is the lower right corner of the plate, the cold water outlet is the upper right corner of the plate, and the cold water medium enters and exits from the lower part; the hot water inlet is at the upper left corner, the hot water outlet is at the lower left corner, the hot water medium is fed in and discharged out from the upper part, and the medium of the heat exchanger is in a pure countercurrent state in the flowing state, so that the heat exchange efficiency can be improved.
In order to further optimize the technical scheme, the mounting, dismounting and maintenance efficiency of the heat exchanger plate is improved, the plate is convenient to dismount at any position on the heat exchanger guide rod, the dovetail groove 4 is formed in the end part of the short side of the base plate 1, the opening width of the dovetail groove 4 is 50-55 mm, and the dovetail groove can be matched with the heat exchanger guide rod.
In the present embodiment, the corrugation depth 332 of the chevron corrugation 33 is 4 to 20mm; the distance between two adjacent herringbone waves 33 is 10-15 mm.
In this embodiment, the protrusions on the flow guiding area 2 are one or more of round, square or drop-shaped. The medium can be led into the heat transfer area for heat exchange by the protrusions.
In this embodiment, the thickness of the substrate 1 is 0.4-0.7 mm, the width of the substrate is 500mm, and the length is 1130mm or 1690mm, and the aluminum zinc copper alloy sheet is manufactured and molded by a die.
When the plate is designed and selected, the plate is provided with a plurality of grooves,
1. Calculating the required physical parameters according to the known process medium and parameters, and calculating the unknown parameters according to a thermal equilibrium equation
(1) The parameters substituted in each formula are values of each side medium at average temperature during general calculation, and when the inlet and outlet data are known, the parameters are obtained by an insertion method;
(2) Heat balance equation qinhale=qput.
Namely: q= Cphqmh (T 1-T2)＝CpCqmC(t2-t1), unit kw, where Cp denotes specific heat (kJ/kg·k), qm denotes mass flow (kg/s), T 1、T2 denotes hot side inlet/outlet temperature, T 1、t2 denotes cold side inlet/outlet temperature, h denotes hot side, c denotes cold side, and the same applies below.
2. Model of primary plate heat exchanger
Substituting the flow velocity v=3.5m/s into a formula(In mm, this formula is suitable for medium water, qv represents the volume flow m 3/h) the angular hole diameter is calculated and then the type of heat exchanger is selected where the angular hole diameter is close to this value.
3. Estimating heat exchange area by assuming the value of the total heat exchange coefficient Ki
(1) The logarithmic average temperature difference Deltatm needs to be calculated, and the countercurrent heat exchange is carried out
(2) Ai=q/Ki Δtm is calculated from the heat exchange amount q=k Δtm a.
4. Determining flow combinations
(1) Calculating the total plate number Np, np=Ne+2, ne refers to the effective heat exchange plate number, ne= [ Ai/a ] (a refers to the effective heat exchange area of the single plate)
(2) Calculating the number of flow channels, nc=np-1
(3) Determining a flow combination, wherein the general heating working condition is a simple flow, and when the number of flow channels is an odd number, the flow combination is generally expressed as: nh and nc represent the number of hot and cold side flow paths, respectively.
5. The flow velocity ωh between the two side plates is calculated,M/s, where f represents the cross-sectional area of the single flow channel (m 2)
If the flow rate between the plates is not in the range of 0.2-0.8m/s, the calculation cannot be continued, and the process is adjusted or the product model is reselected.
6. Calculating Reynolds number Reh, rec
De represents equivalent diameter (m), ρ and μ represent density (kg/m 3) and viscosity (Pa.s) of the medium, respectively
7. Calculating film coefficient
W/m2.k, where λ represents the medium thermal conductivity (W/mk), pr represents the planter number, pr=cp μ/λ
8. Calculation of Kt value
(1) Calculating the sheet resistance Rp, rp=δ/λp, δ representing the sheet thickness (m), λp representing the thermal conductivity of the sheet material
(2)
9. Determining the margin of the margin by comparison with the assumed Ki
If the value is greater than zero and greater than or equal to the required heat exchange area excess, the original assumption is satisfied, and the heat exchange capacity meets the specified requirement; otherwise, if the value is smaller than zero or smaller than the required margin, the Ki value is assumed again, and the calculation is restarted from the step 3 until the value is met; if it is still not satisfied, the product model is re-selected from step 2.
10. Pressure drop check
Δph= Euh ωh2ρh, Δpc= Euc ωc2ρc, unit Pa
If the pressure drop across is less than the nominal pressure drop, the pressure drop check passes, otherwise recalculation is initiated from either step 4 (change flow combination) or step 3 (re-assuming Ki values) or step 2 (re-selecting product models) in sequence.
11. And determining the plate material, the rubber pad material, the design pressure and the like to determine the product model.
In order to further optimize the technical scheme, the circulation smoothness of the medium is improved, and a hydrophobic coating is coated in the diversion area.
Example 2:
Referring to fig. 8 to 10, an embodiment of the present utility model discloses a plate for a plate heat exchanger, which has the same structure as that of embodiment 1, except that the included angle of chevron corrugations is 62 ° or 123 °; the thickness of the substrate 1 is 0.4-0.7 mm, the width of the substrate is 500mm, and the length is 990mm or 1210mm;
The bulges on the flow guiding area are arranged at a certain angle with the herringbone sealing groove, a plurality of bulges are connected end to end, and two adjacent bulges have a certain angle to form a wavy medium flow passage.
Example 3:
Referring to fig. 11 to 13, the embodiment of the present utility model discloses a plate for a plate heat exchanger, which has the same structure as that of embodiment 1, except that the included angle of the chevron corrugations is 57 ° or 127 °; the thickness of the substrate 1 is 0.4-0.7 mm, the width of the substrate is 500mm, and the length is 961mm, 1351mm, 1741mm or 2131mm;
The bulges on the flow guiding area are vertically arranged with the herringbone sealing grooves, the bulges are connected end to end, and the adjacent two bulges are approximately vertical or parallel to form a square medium flow passage.
According to the plate for the plate heat exchanger, the herringbone waves with different angles are selected, so that the plate can be suitable for different working condition combinations, the removing blocks can facilitate the disassembly of the plate, and meanwhile, the dovetail grooves can be disassembled and installed at any position of the guide rod of the heat exchanger, so that the maintenance efficacy of products is improved. Through the arrangement of the herringbone corrugation, the heat exchange coefficient can be improved, and meanwhile, the flow resistance and the pump power of liquid are reduced
In the present specification, each embodiment is described in a progressive manner, and each embodiment is mainly described in a different point from other embodiments, and identical and similar parts between the embodiments are all enough to refer to each other. For the device disclosed in the embodiment, since it corresponds to the method disclosed in the embodiment, the description is relatively simple, and the relevant points refer to the description of the method section.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present utility model. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the utility model. Thus, the present utility model is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (8)
1. A plate for a plate heat exchanger, comprising a base plate (1), characterized in that,
The two ends of the substrate (1) are symmetrically provided with an angular hole area (5), a flow guiding area (2) and a heat conducting area (3); a herringbone seal groove (6) is formed at the joint of the angular hole region (5) and the flow guiding region (2), and an arc line (32) is formed at the joint of the flow guiding region (2) and the heat conducting region (3);
The flow guiding area (2) is provided with a plurality of bulges along the plate surfaces on two sides of the substrate (1), and the bulges are perpendicular to the herringbone sealing groove (6), parallel to the herringbone sealing groove or inclined at any angle;
The heat conduction area (3) is formed by splicing a plurality of detachable removing blocks (31), a plurality of continuous herringbone waves (33) are arranged on the plate surfaces of the removing blocks (31), and the center included angle (331) of the herringbone waves (33) in the horizontal direction is an acute angle, an obtuse angle or a combination of the acute angle and the obtuse angle so as to form three different flow channels.
2. A plate for a plate heat exchanger according to claim 1, wherein the angular hole area (5) is provided with a hot water inlet (51), a cold water outlet (52), a hot water outlet (53), a cold water inlet (54) and a protection corrugation (55), wherein the hot water inlet (51) and the hot water outlet (53), the cold water outlet (52) and the cold water inlet (54) are all symmetrically arranged along the X-axis of the base plate (1), the hot water inlet (51), the hot water outlet (53) and the cold water outlet (52) are symmetrically arranged along the Y-axis of the base plate (1), and the protection corrugation (55) and the flow guiding area (2) are separated by the chevron seal groove (6).
3. A plate for a plate heat exchanger according to claim 1, characterized in that the corrugation depth (332) of the herringbone corrugation (33) is 4-20 mm.
4. A plate for a plate heat exchanger according to claim 1, characterized in that the spacing between two adjacent herringbone waves (33) is 10-15 mm.
5. A plate for a plate heat exchanger according to claim 1, wherein the protrusions are one or more of circular, square or drop-shaped.
6. A plate for a plate heat exchanger according to claim 1, characterized in that the short side end of the base plate (1) is provided with a dovetail groove (4).
7. A plate for a plate heat exchanger according to claim 1, characterized in that the thickness of the base plate (1) is 0.4-0.7 mm.
8. A plate for a plate heat exchanger according to claim 1, characterized in that the base plate (1) is formed by means of a mould from an aluminium zinc copper alloy plate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322959816.4U CN221198142U (en) | 2023-11-02 | 2023-11-02 | Plate for plate type heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322959816.4U CN221198142U (en) | 2023-11-02 | 2023-11-02 | Plate for plate type heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN221198142U true CN221198142U (en) | 2024-06-21 |
Family
ID=91517794
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202322959816.4U Active CN221198142U (en) | 2023-11-02 | 2023-11-02 | Plate for plate type heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN221198142U (en) |
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2023
- 2023-11-02 CN CN202322959816.4U patent/CN221198142U/en active Active
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